Roll reciprocating mechanism



. Sept. 15, 1959 Filed Sept. 7. 1954 H. W. FAEBER ROLL RECIPROCATING MECHANISM 6 Sheets-Sheet l INVENTOR.

HARRY W. FAEBER BY ,SM M x M ATTORNEYS Sept. 15, 1959 H. w. FAVEBER ROLL RECIPROCATING MECHANISM 6 Sheets- Sheet 2 Filed Sept. 7, 1954 g Q2. Hm

INVENTOR.

HARRY W. FAEBER BY Cwm w 3M Tm M ans a NQE ATTORNEYS H. w. FAEBER ROLL RECIPROCATING MECHANISM Sept. 15, 1959 e Sheets-Sheet 5 Filed Sept. 7, 1954 IN VEN TOR.

H A R RY W. FAEBER 3m 2mm 30m ill] lllllll ll J1|l||l|||||lllll|ll|l 1m MA ATTORNEYS P 1 H. w. FAEBER 2,903,966

' ROLL RECIPROCATING MECHANISM 6 Sheets-Sheet 4 Filed Sept. 7, 1954 6 e INVENTOR. '3 I g HARRY W.,FAEBER r BY WM,QMRMQPM ATTORNEYS Sept. 15, 1959 Filed Sept. 7, 1954 6 Sheets-Sheet 5 QoE INVEN TOR. HARRY W. FAEBER "hen,

Sept. 15, 1959 H. w. FAEBER 2,903,966

ROLL RECIPROQATING MECHANISM Filed Sept. 7, 1954 s Sheets-Sheet s INVENTOR. HARRY w. FAEBER United States Patent ROLL REClP-R'OCATING MECHANISM Harry W. Faeber, Larchmont, N.Y., assignor to Time, Incorporated, New York, N.Y., .a corporation of New York Application September 7, 1954, Serial No. 454,535

9 Claims. (Cl. '1-'3'48) This invention relates generally to a printing press ink distributor roll reciprocating mechanism, and more particularly to a reciprocating mechanism of the above noted character which includes a substantially wear-free coupling between the distributor ro'll shaft and the reciprocating drive means.

In a printing press, commonly, ink is transferred to the printing roll from a fountain roll rotating in an ink reservoir through a train of distributor rolls interposed in ink transferring relation between the printing roll and the fountain roll. To assure deposition of a uniform ink film upon the printing roll, some of the several distributor rolls in the train thereof, in addition to their rotation, are generally given a reciprocating motion in the axial direction. By virtue of this reciprocating action, the ink in the course of its transfer through the distributor roll train is worked back and forth between the various distributor roll surfaces to emerge as a homogeneous ink film upon the surface of the last roll.

The distributor roll reciprocating mechanisms of the prior art are subject to various disadvantages. For example, since reciprocating motion involves rapid changes in direction, the motion transmitting coupling between the distributor rolls and the source of the reciprocating motion has previously been subject to a considerable amount of wear. Moreover, the prior art mechanisms have not utilized opposed vibration of adjacent rollers and have not been altogether satisfactory in converting a rotary motion at one stage in the motion transmission into a linear reciprocating motion and conversely. Additionally, the prior art mechanisms have been cumbersome and ineflicient in that they occupy more space and employ a great many more parts than are desirable.

It is accordingly an object of this invention to provide a distributor roll reciprocating mechanism free of the above enumerated disadvantages.

It is another object of this invention to provide in a mechanism of the above-noted character, substantially wear-free coupling between the source of reciprocating motion and the member to be reciprocated.

A further object of this invention is to provide in a mechanism of the above-noted character a motion transmission unit which efiiciently converts rotary motion into reciprocating motion and conversely.

A still further object of this invention is to provide a simple and compact distributor roll reciprocating mechanism.

These and other objects of the invention will be better understood from a following detailed description of a representative embodiment thereof taken in conjunction with the accompanying drawings in which:

Figure l is a plan view of a distributor roll reciprocating mechanism;

Figure 2 is a side elevation of the mechanism taken in cross section as indicated by the arrows 22 of Figure 1;

Figure 3 is .a front elevation of the mechanism taken in cross section as indicated by the arrows 33 in Figure l;

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Figure 4 is a cut-away plan view of the mechanism wherein the upper parts have been removed to expose the lower parts as indicated by the arrows 4-4 in Figure 2;

Figure 5 is a fragmentary plan view, taken in a horizontal cross section plane through the axis of a distributor roll shaft, of a portion of a motion transmission unit used in the distributor roll reciprocating mechanism;

Figure 6 is a side elevation, partially in cross section of a modification of the invention, and

Figure 7 is a partially sectioned plan view of the modification of Figure 6.

In the description to follow it will be understood that like parts are designated by the same number with different letter suffixes attached thereto, and that unless otherwise noted, a description of one part applies as properly to a similarly numbered part.

Referring now to the figures, the numbers 10, 1 1, 12 and 13 (Fig. 1)., respectively, designate separate distributor rolls in a train thereof adapted in a printing press to be interposed between a printing roll and a fountain roll, neither of which are shown. In the mentioned train, the odd distributor rolls 11 and 13 have metallic peripheral surfaces while the even distributor rolls 10 and 12-are covered with jackets 14 and 16 of a rubberlike material. The peripheral surfaces of the various rolls are in frictional contact to provide for ink transfer from, say, roll 10 to roll 13 upon rotation of the rolls. The various rolls may be rotated in a suitable manner as for example, by gears (not shown) at the opposite end of rolls 11 and 13. The rolls 11 and 13 drive the rolls 1t) and 12 through frictional coupling.

Rolls 10, 11, 12 and 13 are respectively mounted on a set of hollow shafts 20a, 20b, 20c, 20d journalled for both free rotary and axial movement, the shafts being received at one end within suitable journalling means (not shown) and at the other end'within journalling means annexed to the roll reciprocating mechanism. Considering these latter mentioned journalling means in more detail, a side frame 21 (Figures 1 and 2) has formed therein separate bores lined with bushings 22b and 22d forming respective bearing surfaces for shafts 20b and 20d which enterside frame 21 on the side thereof near the distributor rolls, the mentioned shafts extending through and beyond the side frame so that the shaft ends lie outward of the far side of the side frame.

Side frame 21 supports secured to its top surface along the lengthwise outside margins thereof a set of spacer blocks 23 disposed to define between themselves (Fig. 4) a central lengthwise channel 24 along the top of side frame 21 and a set of intra-block openings 25 lying along both sides of the central channel. The spacer blocks 23 in turn support, overhead, a mounting plate 26 co-extensive with the top of side frame 21. Mounting plate 26 has formed in its upper surface a shallow guide way 27 above which are disposed two bearing assemblies 28a and 280. Bearing assemblies 28a and 28c may be supported in a manner as disclosed in my copending US. application, Serial No. 441,418, filed July 6, 1954, to permit the rubber covered distributor rolls 10 and 12 to move up and down for automatic adjustment of their contact with the steel distributor rolls 11 and 13.

Considering now the distributor roll reciprocating mechanism proper, the shaft 20a (Fig. 5) has mounted thereon between side frame 21 and the distributor rolls a concentric sleeve 32a maintained in freely rotatable but fixed axial relation with shaft 20a by an appropriate means, as, for example, a ball bearing assembly 33a interposed between sleeve 32a and shaft 20a. Bearing assembly 33a may be secured in place on shaft 20a in a conventional manner as, for example, by the split collar 34a fitted into a circular groove on the shaft. The exterior surface of sleeve 32a is machined to exhibit a set of peripheral annular faces 35a, 36a, 37a, 38a of which at least two faces as, for example, faces 36a and 37a are at an angle to the shaft axis and respectively face leftward and rightward as referred to the shaft axis. The mentioned annular faces may be disposed to form, for example, a set of annular gear teeth 39a, 40a, the set of gear teeth forming an annular rack.

The sleeve 32a is adapted to be given an axial reciprocating motion by a movable motion imparting means which is disposed proximate the sleeve, has components of motion of opposite senses in the direction of the sleeve axis, and alternately makes pressure engagements with firstione and then the other of the mentioned leftward and rightward facing annular faces of the sleeve. This motion. imparting means may take, for example, the form of a pinion means such as a segment gear 45a having teeth 46a, 47a, 48a which mesh in conventional gear relation with peripherally local portions of the annular teeth 39a, 40a. Segment gear 45a is secured by a split hub portion 49a of the segment gear and a bolt 50a to a stub shaft 51a for rotation in fixed relation therewith (stub shaft 51a being mounted in a manner to be later described).

In operation, stub shaft 51a is given a rapid oscillatory motion which is converted through segment gear 45a and sleeve 32a into a rapid reciprocating motion of the distributor roll shaft 20a. In the course of this reciprocating motion, during each stroke while the gear teeth are transmitting the force necessary to move the roll in one direction, sleeve 32a does not rot-ate, and thus there is no annular sliding of the gear teeth under load. However, since sleeve 32a is in freely rotatable relation with shaft 20a, the repeated momentary load relief occurring at each reversal of the gear tooth pressure, allows a stepby-step rotary creep of sleeve 32a with respect to the engaging segment gear. The rotary creep described has the efiect of continuously bringing fresh peripherally local portions of the annular teeth 39a and 40a into meshing relation with the teeth of segment gear 45a. As a result, the wear arising from normal gear tooth action during the reciprocation of sleeve 32a is distributed over the entire peripheral surface of the sleeve to accordingly extend exceedingly the useful life of the sleeve.

With regard to the above-described pinion means cou pling between stub shaft 51a and distributor roll shaft 204, it should be noted that while the stub shaft motion is rotary and the shaft motion, in contrast, is linear, the combination of the pinion means (segment gear 45a) meshing with the annular rack on the sleeve 32a efliciently converts the one type motion into the other, since the force imparting components of motion of the segment gear are the tangential motion components thereof at the point of effective engagement with the annular rack described, these tangential motion components always acting substantially in one or the other of the directions of the sleeve axis except for the small separating force due to the pressure angle of the gear teeth.

Considering now the mounting for stub shaft 51a (as best seen in Fig. 2) the upper and lower ends of the stub shaft are respectively journalled into suitable means such as, say, ball bearing assemblies 55a and 56a to be supported thereby for free rotation. Stub shaft 51a is held in fixed axial relation with the bearing assemblies 55a, 560 by a first lower flange 57a integral with the stub shaft and a second upper flange 58a detachable from the stub shaft by a bolt 59a, the mentioned flanges each being in clamping relation with the inner race of the bearing assembly adjacent thereto. The bearing assemblies 55a, 56a are secured in a conventional manner within and at opposite ends of a cylindrical bore formed in a peripherally rounded end portion 60a of a bearing assembly' mounting 61a. The mentioned cylindrical bore is interiorly closed around its periphery with the exception of midway of the ends of the bore where a portion of the portion 60a facing the sleeve 32a is cut away to form a window exposing the interior of the bore. The gear segment 45a passes through this window to mesh with the teeth on sleeve 32a.

In addition to carrying the segment gear 45a, the stub shaft 51a at its lower extremity carries the means by which the stub shaft is driven in rotation, this shaft driving means taking the form, for example, of a pinion means such as a segment gear 62a extending away from the stub shaft at right angles to the center radius of segment gear 45a. Conveniently, segment gear 62a may be made integral with stub shaft 51a, the stub shaft, the lower flange 57a thereof and the segment gear 62a being a unitary member. Segment gear 62a is so disposed and of suflicient extent to pass through an opening 25 between two adjacent spacer blocks 23, the teeth 63a of the segment gear lying within the channel 24. In a manner later described and by virtue of a meshing relation of teeth 63a, the segment gear 62a is adapted to be driven in rotary oscillation.

The bearing assembly mounting 61a, along with the rounded end portion 60:: includes, in addition, a flat base portion 65a and a vertical rib portion 66a upstanding from this base portion, the rib 66a flaring outwardly at one end to merge with the rounded end portion. Conveniently, the described bearing assembly mounting 61a may be secured to the rest of the roll reciprocating mechanism by a set of bolts 67a passing through the base portion 65a and into the mounting plate 26.

The assembly consisting of gear segment 45a, shaft 51a and ball bearings 55a is secured against endwise (up and down) movement by shoulder 60b, outer race spacer 60c and top retainer cover 700. The latter is fastened to 60a by screws like the one shown at 71a.

The description so far has outlined a motion transmission unit for reciprocating the distributor roll shaft 20a through reciprocation of the sleeve 32a mounted thereon, the term motion transmission unit including, for example, segment gears 45a and 62a, stub shaft 51a which links the two segment gears in rotation and whatever other elements are necessary, as described, for the operation of the segment gears and stub shaft. Reference to the drawings (particularly Figs. 1 and 3) will indicate that shaft 200 is reciprocated likewise, the sleeve 32c therefor being similarly mounted between the side frame 21 and the distributor rolls, and being similarly driven by a substantially identical motion transmission unit.

The steel distributor roll shafts 20b and 20d are reciprocated by means similar to that described above, excepting certain minor changes to be now pointed out. In contrast to sleeves 32a and 32c, sleeves 32b and 32d lie to the far side of side frame 21 as referred to the distributor rolls, the motion transmitting units for these latter sleeves being similarly disposed. Moreover, the motion transmitting units on the far side of the side frame differ slightly from these on the near side thereof, the differences being best shown in Fig. 2. Note in this figure that stub shaft 51b and its associated elements are generally in upside-down relation to stub shaft 51a and the elements associated therewith. Moreover, note that segment gear 62a is detachable from stub shaft 51b, being secured thereto by a bolt 64b passing through a split hub portion of the segment gear, that the lower side of segment gear 62b proximate the stub shaft forms one of the flanges securing the stub shaft in fixed axial position, and that rather than being fitted within the same continuous bore, the bearing assemblies 55b, 56b are secured, conventionally, in fitted relation within the separate bores of two spaced apart brackets 75b, 76b, secured in a con ventional manner to the side of side frame 21 away from the train of distributor rolls. As shown in Figure 2, bracket 75b may be formed from a single member, while bracket 76b may be conveniently built up out of the '5 members 77b, 78b, 79b, 80b, 81b (Fig. 3), and the bolts 82b. Also, parts 75b, 77c and 76c may be one solid integral piece.

Referring now to the means for producing the oscillatory rotations of the several stub shafts, the side frame 21 has formed in the upper side thereof a lengthwise running slot 84 of rectangular cross section. To one end of side frame 21 there is secured by bolts 84' a bracket 85 with its upper side formed to continue the slot 84 out beyond the end of the side frame proper or bracket 85 may preferably be an integral part of the side frame. The slot 84, itself, is adapted to act as a bed and guide way for a lower rack bar 86, movable back and forth in endwise manner within the slot.

Lower rack bar 86 has formed at the end thereof near bracket 85 a set of upstanding gear teeth 87 defining a horizontal rack 88. Rack 88 meshes with a segment gear '89 mounted on and for rotation with a stub shaft 90 journalled into an appropriate bearing assembly 91, the stub shaft 90 being drivable by an eccentric arm 92, keyed to shaft 90, and coupled with a linkage 93. The linkage 93 in turn is driven from a source of mechanical motion (not shown) such as a rotating crank of adjustable eccentricity, for example.

The lower rack bar 86 carries secured to the top thereof by bolts .100, an upper rack bar 101 occupying the channel 24 running between the spacer blocks 23, the two rack bars being reciprocable together in endwise movement to provide a common driving member for reciprocating (through the described motion transmission units) all of the distributor roll shafts. As an exemplary coupling between this common driving member and the motion transmission units, the upper bar 101 may have formed along the side thereof towards the distributor rolls a first linear rack 102a and a second linear rack 1020', the mentioned racks being respectively disposed opposite separate gaps 25 between the spacer blocks 23 positioned along the mentioned side. Similarly, upper rack 101 may have formed in the side thereof away from the distributor rolls a third linear rack 102b and a fourth linear rack 102d, these last-mentioned racks also being respectively disposed opposite separate gaps 25 between the set of spacer blocks 23 on the side of base block 21 away from the distributor rolls. The teeth of each of the described linear racks are adapted to mesh with the teeth of the driving segment gear of the corresponding motion transmission unit, segment gear 62a, for example, meshing with linear rack 102a. In a preferred alternative, rack bars 86 and 101 may be formed in one integral bar, rack 88 being on top, and racks 10211, b, c and d on the side surfaces of a single bar of rectangular cross section.

In operation linkage 93, when reciprocated by a source of mechanical motion (not shown) will, through eccentric arm 92 and stub shaft 90, produce an oscillatory motion of segment gear 89. The oscillatory motion of segment 89 will in turn, by virtue of the meshing engagement thereof with rack 88, be converted into an endwise reciprocating movement of the lower rack bar 86 and upper rack bar 101. As upper bar 101 reciprocates the linear rack 102a thereof, for example, will, through its meshing engagement with segment gear 62a produce a rotary oscillatory motion of the segment gear. The oscillatory motion just described is transmitted by stub shaft 51a to segment gear 45a which oscillates correspondingly. The oscillation of segment gear 45a will, by virtue of the meshing of the teeth thereof, with the annular teeth on sleeve 32a, be converted into an axial reciprocating motion of distributor roll shaft20a, and of course, the latter reciprocating motion is imparted to the distributor roll itself.

In like manner, the motion transmitting unit including segment gear '620, stub shaft 510 and segment gear 450 will cause a reciprocation of distributor roll 12 which is ciprocation of distributor roll 10. The motion transmitting units for distributor rolls 11 and 13, however, by virtue of their location on the opposite side of upper rack bar 101iproduce reciprocations of these distributor rolls 11 and 13 which, while mutually similar and mutually directionally in phase, are of opposite phase as compared to the reciprocations of the distributor rolls 10 and 12. Thus, it will be seen that in the train of'distributor rolls, the even distributor rolls'undergo a reciprocation of reference phase and the odd distributor rolls undergo a reciprocation of opposite phase. By virtue of the'described oppositely phased reciprocations of alternate distributor rolls in ink transferring contact, the ink transferred through the distributor roll train undergoes a cumulative spreading in the course of transfer in the manner and with the advantages disclosed in my US. Patent No. 2,703,050, issued on March 1, 1955 and entitled, Vibrator Mechanism.

As previously described by virtue of the reversing thrust arising from the distributor roll reciprocations, the sleeves mounted on the distributor roll shafts, as for example, the sleeve 32a, undergo, in the course of operation, a rotary creep so that fresh portions of the annular teeth thereof progressively come into meshing engagement with the teeth of the segment gear driving the sleeve. By this means, the wear on the sleeve is distributed over the entire peripheral surface thereof to provide an exceedingly long life for the sleeve before replacement thereof is necessary.

As also. previously described, the reciprocating motion of a common driving member, specifically the member composed of lower rack bar 86 and upper rack bar 101, is efliciently converted into reciprocating motions ofa plurality of members, specifically, the distributor roll shafts, bya plurality of motion transmission units which respectively couple the plurality of driven members with the common driving memben'each motion transmission unit including, for example, two circular segment gears linked in rotation by a shaft, one of the segment gears engaging with a linear rack onthe common driving member and the other segment gear engaging with a rack affixed to the associated-driven member. As is well known, a rack and pinion in meshed relation will convert a reciprocating motion to a rotary oscillatory motion, and vice versa, with substantially no loss in efficiency. Hence, by the system described, the reciprocating motion of the common driving member is converted into reciprocating motions of a plurality of driven members in an efficient manner.

It should also be noted that the described invention provides an eflicient and compact structural organization for a distributor roll reciprocating mechanism in that, as a space saving expedient, the common driving means for the distributor rolls (namely lower rack bar 86 and upper rack bar 101) passes between the upper level distributor roll shafts and the lower level distributor roll shafts. Further space saving is achieved by providing that the common driving means passes inside the shaft ends for one of the distributor roll levels (for example, the ends of shafts 20b, 20d), and by providing that the motion transmitting units coupling the common driving means with the several distributor roll shafts are distributed half to one side and half to the other of the common driving means so that both sides of the common driving means may be utilized to operate the motion transmitting units. Moreover, a further advantage is afforded by the described structural organization in that the mentioned distributive relationship of the motion transmitting units to the distributor roll shafts and to the common driving means therefor permits oppositely phased reciprocations of alternate distributor rolls to be obtained by the use of substantially identical motion transmitting units, each unit employing only a minimum number of components.

In Figures 6 and 7 which show another embodiment of the invention, the top surface of the side frame 21 and the side -wall thereof away from the distributor rolls are respectively cut away to form a lengthwise rabbet 110.

similar to and directionally in the same phase as the re- 7 For support of the several elements of the roll reciprocat- 'ing mechanism there is provided an auxiliary frame 112 attached to side frame 21 byconventional fastening means (not shown). 1 The frame 112 is in the nature of a cast unitary member comprising a horizontal plate-like web 113 overlying the topsurface of side frame 21, and a vertical plate-like web 114 extending above web 113 and also below web 113 in flush relation with the side wall of side frame 21. In addition auxiliary'frame 112 includes (Fig. 6) three horizontal shelf-like brackets 115, 116 and 117 extending from web 113 away from the side wall of side frame 21. Bracket 115 which is of the largest lengthwise extent is located at the levelof web 113 while brackets 116 and 117 are respectively located above the center of bracket 115 and below the left-hand side of bracket 115. In Figure 7, for clarity of the drawing, the major portion of bracket 116 is broken away while the bracket 117 is not shown.

In Figure 7 it will be noted that for the marginal portion of web 114 lying above web 113 the margin 118 of web 114 is flanged such that the margin 118 I lies in the same plane as the side wall of side frame 21.

Accordingly the margin 118 of web 114 and the side wall of side frame 21 together provide a flat seating for an oil-tight housing 120 which, as shown in section in both Figures 6 and 7, completely encloses the several moving elements of the roll reciprocating mechanism.

As seen in Figures 6 and 7 the web 113 overlies rabbet 110 while the web 114 encloses the rabbet from the side so that rabbet 110 and webs 113 and 114 together define an enclosed guideway of rectangular cross section for the heretofore discussed rack bar 86. In the presen'tly described embodiment, lengthwise reciprocation of the rack bar 86 in its guideway is accomplished by a connecting rod 121 which is reciprocated (by an element not shown) to oscillate a rocker arm 122 with which the rod 121 is connected by a pin 123 and by a clevis 124 formed in the rocker arm. Rocker arm 122 is afiixed on a rocker shaft 125 which is journalled for rotation by means of a bearing 126 (Fig. 7) in web 114 on one side of rack 86 and by another bearing 127 in a bearing block 128 mounted on web 113 on the other side of rack 86. Between bearing 126 and 127 the rocker shaft 125 carries for rotation therewith the heretofore described segment gear 89 which passes through a window 130 in web 113 to mesh with the horizontal rack 88 of rack bar 86. Thus the reciprocations of connecting rod 121 are converted through rocker arm 122, rocker shaft 125 and segment gear 89 into lengthwise reciprocations of the rack bar 86.

To convert the lengthwise reciprocations of rack bar 86 into corresponding reciprocations of the shafts 20a and 20c for the rubber-covered distributor rolls and 12, there is provided a motion transmission unit including a vertical rocker shaft 135 (Fig. 6) which is journalled for rotation at its upper end by a bearing 136 assembly in bracket 116 and is also journalled for rotation at an intermediate point by a bearing assembly 137 in bracket 115. Rocker shaft 135 extends through I bracket 115 to carry below this bracket a sector gear 138 keyed to the shaft 135 and extending through a window 139 in web 114 to mesh with a linear rack 140 formed on the side of rack bar 86.

Rocker shaft 135 in addition carries a keyed pinion 145 which meshes with the annular-toothed sleeve 32c in the same manner as, in the embodiment of Figs. 1-6, the segment gear 450 (Fig. 1) meshes with the sleeve 320. In the presently described embodiment however the sleeve 32c rather than being mounted directly upon shaft c is, instead, mounted in axially fixed but freely rotatable relation upon a separate slide shaft 1460. Shaft 146a is supported to either side of sleeve 1460 by a pair of bushings 147a and 1480 (shown in section in Fig. 7) .which journal the slide shaft to permit free axial movement thereof. Of these bushings, the bushing 8 1470 is fitted within web 114'while the bushing 1480 is fitted within a bearing block 1490 formed as an upturned end of the bracket 115. Key 1460' allows shaft 1460 to reciprocate but secures it against rotation. A similar key is provided (but not shown) for shaft 146a.

To impart the axial motion of slide shaft 1460 to the shaft 20c, the bushing 1470 passes the slide shaft 1460 through the web 114, the shaft terminating at its inboard end in the form of 1a T-slot head 150a (Fig. 7). The T-slot head 150a receives a ball bearing assembly 1510 mounted upon the end of shaft 20c such that shafts 1460 and 20c are coupled together for axial movement so that shaft 200 is free to rotate while shaft 146a does not rotate.

In operation it will be seen that as rack bar 86 is caused as described to reciprocate lengthwise, the reciprocations thereof, by way of linear rack 140, sector gear 138, vertical rocker shaft 135, pinion 145, sleeve 1520, slide shaft 146e, T-slot head 150e, ball bearing assembly 151c and shaft 200 will be converted into corresponding reciprocations of the rubber covered roll 12.

To obtain similar reciprocations in the same phase for the rubber-covered roll 10, the pinion 145 meshes with an idler pinion 155 which in turn meshes with the annular-toothed sleeve 32a on the slide shaft 146a. For support of the idler pinion 155 a fixed shaft 156 extends vertically between brackets and 116 (Fig. 6), the idler pinion 155 being mounted for free rotation about this shaft by a pair of bearing assemblies 157 and 158. As pinion oscillates to impart a reciprocating motion to sleeve 320, the pinion 145 by way of idler pinion will impart a corresponding reciprocating motion in the same phase to annular-toothed sleeve 320. Since sleeve 32a is mechanically coupled to shaft 20a in a manner the same as sleeve 320 is coupled to shaft 200, it will be seen that the rubber covered rolls 10 and 12 will be given co-phasal reciprocations.

To convert the lengthwise reciprocations of rack bar 86 into reciprocations of the steel rolls 11 and 13 which are mutually of the same phase but are of opposite phase With respect to the reciprocations of rolls 10 and 12, there is provided another motion transmitting unit which includes a fixed shaft 160 (Fig. 6) extending vertically between the brackets 115 and 117. The fixed shaft 160 carries as a unitary member a sector gear 161, a pinion 162 and a sleeve 163 connecting the pinion and the sector gear. A freely rotatable mounting of the unitary member about the fixed shaft 160 is provided by a pair of bearing assemblies 164 and 165 (Fig. 6). Of the aforementioned parts of the unitary member, the sector gear 161 passes through a window 166 in web 114 to mesh with a second linear rack 167 formed on the side of rack bar 86, while the pinion 162 meshes with the annular-toothed sleeve 32b on the shaft 20b for the steel roll 11. Thus, lengthwise reciprooations of rack bar 86 will, by way of linear rack 167, sector gear 161, sleeve 1'63, pinion 162 and annular-toothed sleeve 32b, cause corresponding reciprocations of the shaft 20b.

It will be noted that the reciprocations imparted to shaft 20b are of opposite phase to the reciprocatious imparted to shaft 200. This mode of operation follows from the fact that, while the pinions 145 and 162 always have the same rotation direction, the annular-toothed sleeve 32c meshes with pinion 145 at the right-hand side thereof, Whereas the annular-toothed sleeve 32b meshes with pinion 162 at the left-hand side thereof. Hence although pinions 145 and 162 have the same direction of rotation, the tangential components of motion imparted by these pinions to their respective sleeves 32c and 32b will be of opposite direction.

For reciprocation of the shaftv 20d,"a fixed shaft 170 (Fig. 6) extending vertically between brackets 115 and 117 carries by means of a bearing assembly 171 an idler pinion 172 which is freely rotatable about the fixed shaft 171'). The pinion 172 meshes on: one side with the pinion 162 and meshes on the other side with the annular-toothed sleeve 32d mounted, as heretofore described, upon the shaft 200! for the steel rolliiii. As pinion 162 oscillates to reciprocate sleeve 32b,'the motion ofepinio'n 162 is converted by way of idler'pinion172 into a reciprocation of sleeve 32d of common phase withthat of sleeve 32b.

For proper operation of the train of distributor rolls 1t), 11, 12, 1.3, the steel rolls 11 and 13 should be water cooled. To permit flow of water to the interiors of the rolls 11 and 13, the hollow shafts 20b and 20d are equipped with respective hollowextensi'ons 175 and 176 which pass through the housing120for the roll reciprocating mechanism by way of respective glands 177 and 178 fitted in the housing 120. The glands 177 and 178 while providing an oil-tight .seal permit both axial and rotary motion of the shaft extensions 175 and 176 respectively passing therethrough. Exterior of the housing 12% the mentioned shaft extensions 175 and 176 are connected to a cooling water supply by rotary joints (not shown).

The above described embodiment of the invention shown in Figures 6 and 7 is advantageous in a number of respects. For example, by location of the entire roll reciprocating mechanism to one side of the rack bar 86, it is possible toenclose the entire mechanism by the oiltight housing 120 such that the moving elements of the mechanism may be lubricated Without undesirable spraying or leakage of oil onto other parts of the printing press. Also, by coupling the annular-toothed sleeves 32a and 320 to the shafts 20a, 200 by way, respectively, of the slide shafts 146a, 1460, the T slot heads 150a, 1500 and the ball bearing units 151a, 1510, the rubber-covered rolls 10 and 12 maybe easily removed by simply detaching the shafts 20a, 20c fromtheir couplings with the T-slot heads 156a, 150a. This is madepossible by the open T-slots which allow the bearing 1510 to slide upward out of engagement as the roll 12 is lifted out of the press. The ability to detach shafts 20a, 20c in this manner is advantageous since it permits removal of the rubber covered rolls 1%), 12 without the need for disassembling a large part of the roll reciprocating mechanism.

It will be understood that .the specific embodiment described above and shown in the drawings is acceptable of numerous modifications in form :and detail within the spirit of the invention. Therefore, the invention is not to be thought of as restricted to the embodiment shown, but rather as broad as the scope of the following claims will permit.

I claim:

1. Printing press apparatus'for providing as a cumulative effect a spreading of ink into a uniform film upon transference of said ink through an odd and even distributor roll train wherein each distributor roll is supported in axially fixed relation with an axially movable shaft means, said apparatus comprising separate annular rack means carried in concentric relation to and coupled with each shaft means in fixed axial but freely rotatable relation therewith, each annular rack means being comprised of a plurality of annular teeth encircling the associated shaft means, separate pinion means respectively associated with said shaft means and rack means, each pinion means being mounted for rotary movement about an axis transverse to the associated shaft means and each pinion means having teeth with contact faces which are also transverse to the last-named shaft means, said pinion means respectively engaging through their teeth with a peripherally local portion of the teeth of the associated annular rack means, the couplings of said pinion means and said rack means permitting random rotation of each rack means about the axis of the associated shaft means, linear rack means cyclically reciprocable in endwise motion, and motion coupling means coupled between said linear rack means and said pinion means to convert the cyclical reciprocations of said linear rack means into oppositely phased axial reciprocations of the odd and even distributor roll shaft means, each pinion-means during said cyclical reciprocations vibrating the associated annular rack means to induce therein a rotary creep to successively present a fresh portion of the teeth thereof to the teeth of the pinion means in engagement therewith.

2. Printing press apparatus for providing as a cumulative eflect a spreading of ink intoa uniform film upon transference of said ink through an odd and even distributor roll train wherein each distributor roll is supported in axially fixed relation with an axially movable shaft means, said apparatus comprising annular rack means mounted upon each shaft means in fixed axial but freely rotatable relation therewith, a motion transmitting unit for each odd distributor roll shaft means including a first pinion means engaging with a peripherally local portion of the annular rack means on the shaft means and a second pinion means fixedly linked in rotary motion with said first pinion means, a similar motion transmitting unit for each even distributor roll shaft means, and a rack bar cyclically reciprocable endwise and carrying 'on opposite sides thereof separate racks respectively engaging the second pinion means associated with said odd and even shaft means, each annular rack means during said cyclical reciprocation undergoing a rotary creep to successively present a fresh portion thereof to the first pinion means in engagement therewith.

3. Painting press apparatus for providing as a cumulative effect a spreading of ink into a uniform film upon transference of said ink through an odd and even distributor roll train wherein each distributor roll is sup ported in axially fixed relation with an axially movable shaft means, said apparatus comprising, annular rack means mounted upon each shaft means in fixed axial but freely rotatable relation therewith, a motion transmitting unit for each pair of odd distributor roll shaft means, said unit including a pair of meshed pinion means respectively engaging the two annular rack means on the pair of shaft means, said unit also including a third pinion means fixedly linked in rotation with one of said pair of first named pinion means, a similar motion transmitting unit for each pair of even distributor roll shaft means, and a rack bar cyclically reciprocable endwise and carrying separate racks respectively engaging the several second pinion means within the several motion transmitting uni-ts, each annular rack means during said cyclical reciprocation undergoing a rotary creep to successively present a fresh portion thereof to the pinion means in engagement therewith.

4-. Printing press apparatus for providing as a cumulative effect a spreading of ink into a uniform film upon transference of said ink through an odd and even distributor roll train wherein each distributor roll is supported in axially fixed relation with an axially movable shaft means, said apparatus comprising a sleeve concentric with each shaft means, each sleeve having formed in the surface thereof a set of annular teeth in rack relation, ball bearing coupling means interposed between each sleeve and shaft means to retain the sleeve in fixed axial but freely rotatable relation therewith, a motion transmitting unit for each odd distributor roll shaft means including a first pinion gear meshing with peripherally local portions of the teeth on the sleeve, a second pinion means, and "a member fixedly linking said first and second pinion means in rotary motion, a similar motion transmitting unit for each even distributor roll shaft means, a rack bar cyclically reoiprocable endwise and carrying on opposite sides thereof separate racks respectively engaging the second pinion means associated with said odd and even shaft means, each sleeve during said cyclical reciprocation undergoing a rotary creep to sue cessi-vely present fresh portions of the annular teeth thereof to the first pinion means in engagement therewith.

Printing press apparatus forproviding as a cumulative effect a spreading of ink into a uniform film upon transference of said ink through a train of alternating upper and lower'level distributor rolls can-led in axially fixed relation upon respective mounting shafts, said apparatus comprising, a plurality of slide shafts aligned with and detachably coupled with the mounting shafts lying at one of said levels, annular rack means carried in concentric relation to and coupled with each mounting shaft in fixed axial but freely rotatable relation therewith, the annular rack means respectively associated with the mounting shafts at said one level being coupled therewith by way of said slide shafts, separate pinion means respectively engaging with a peripherally local portion of each annular rack means, linear rack means cyclically reciprocable in endwise motion, and motion coupling means coupled between said linear rack means and said pinion means to convert the cyclical reciprocation of said linear rack means into oppositely phased axial reciprocations of the upper and lower level mounting shafts, each annular rack means during said cyclical reciprocation undergoing a rotary creep to successively present a fresh portion thereof to the pinion means in engagement therewith.

, 6. Printing press apparatus for providing as a cumulative effect a spreading of ink into a uniform film upon transference of said ink through a train of alternating upper and lower level distributor rolls carried in axially fixed relation upon respective mounting shafts, said apparatus comprising, a plurality of slide shafts aligned with and detach'ably coupled with the mounting shafts lying at one of said levels, annular rack means carried in concentric relation to and coupled with each mounting shaft in fixed axial but freely rotatable relation therewith, the annular rack means associated with the mounting shafts at said one level being coupled therewith by way of said slide shafts, a motion transmitting unit for each pair of mounting shafts at said upper level, a given @unit including a pair of meshed pinion means respectively engaging the two annular rack means coupled with the pair of upper level mounting shafts, the given unit also including a third pinion means fixedly linked in relation with one of said pair of first-named pinion means, a similar motion transmitting unit for each pair of lower level mounting shafts, and a rack bar cyclically reciprocable endwise and carrying separate racks respectively engagingthe several second pinion means within the several motion transmitting units, each annular means during said cyclical-reciprocation undergoing a rotary creep to successively present a fresh portion thereof to the pinion means in engagement therewith.

7. Printing press apparatus for providing as a cumulative effect a spreading of ink into a uniform film upon transference of said ink through an odd and even distributor roll wherein each distributotr roll is supported in axially fixed relation with an axially movable shaft means, said apparatus comprising separate annular rack means respectively carried in concentric relation to and coupled with said shaft means in fixed axial but freely rotatable relation therewith, separate pinion means respectively engaging with a peripherally local portion of each annular rack means, linear rack means lying between said distributor rolls and said several annular rack means, said linear rack means being cyclically reciprocable in endwise motion, motion coupling means coupled between said linear rack means and said pinion motion coupling means.

8. Printing press apparatus for providing as a cumulative effect a spreading of ink into a uniform film upon transference of said ink through a train of alternate upper and lower level distributor rolls wherein said distributor rolls are respectively supported in axially fixed relation by a set of axially movable parallel shaft means, said apparatus comprising a common driving member extending perpendicular to and through said shafts between the upper level and lower level therefor and between said distributor rolls and the ends of the shaft means at one of said levels, a first plurality of motion transmitting units disposed tothe far side of said driving member with respect to said rolls for converting the reciprocating motion of said member into respective reciprocations of the shafts at said one level, and a second plurality of motion transmitting units disposed to the near side of said driving member with respect to said rolls for converting the reciprocating motion of said member into respective reciprocations of the shafts at the other level.

9. Printing press apparatus for providing as a cumulative effect a spreading of ink into a uniform film upon transference of said ink through a train of alternate upper and lower level distributor rolls wherein said distributor rolls are respectively supported in axially fixedrelation by a set of axially movable parallel shaft means, said apparatus comprising a common driving member with rack means on both sides thereof, said member extending perpendicular to and through said shaft means between the upper and lower level shaft means and also between said rolls and the ends of the shaft means at one of said levels, a plurality of rack means for axially moving said shaft means, said rack means being mounted on the shafts at said one and the other level, respectively, to the far and to the near side of said member as re ferred to said rolls, and a corresponding plurality of similarly disposed motion transmitting units respectively coupling each of said last-named rack means with an adjacent rack means on said member, each unit including a pinion means meshing with a driving member rack means, a pinion means meshing with a shaft-mounted rack means, and a linkage which links said two pinion means in rotation, the several motion transmitting units being adapted to convert the reciprocating motion of said driving member into oppositely phased reciprocations of alternate distribution rolls.

References Cited in the file of this patent UNITED STATES PATENTS 580,984- Meisel Apr. 20, 1897 853,753 Bechman May 14, 1907 886,367 Harris et al. May 5, 1908 1,074,066 Rea Sept. 23, 1913 1,450,269 Walser et a1 Apr. 3, 1923 1,860,496 Droitcour May 31, 1932 2,581,687 McWhorter Jan. 8, 1952 

